WO2013102951A1 - Vanne papillon - Google Patents

Vanne papillon Download PDF

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Publication number
WO2013102951A1
WO2013102951A1 PCT/JP2012/000037 JP2012000037W WO2013102951A1 WO 2013102951 A1 WO2013102951 A1 WO 2013102951A1 JP 2012000037 W JP2012000037 W JP 2012000037W WO 2013102951 A1 WO2013102951 A1 WO 2013102951A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
housing
butterfly valve
valve according
guide member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2012/000037
Other languages
English (en)
Japanese (ja)
Inventor
横山　雅之
克典 高井
暁 長谷川
綿貫　晴夫
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2012/000037 priority Critical patent/WO2013102951A1/fr
Priority to JP2013552330A priority patent/JP5714135B2/ja
Priority to US14/350,423 priority patent/US20140252259A1/en
Publication of WO2013102951A1 publication Critical patent/WO2013102951A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/224—Details of bearings for the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • F02M26/26—Layout, e.g. schematics with coolers having bypasses characterised by details of the bypass valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/66—Lift valves, e.g. poppet valves
    • F02M26/67—Pintles; Spindles; Springs; Bearings; Sealings; Connections to actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/66—Lift valves, e.g. poppet valves
    • F02M26/69—Lift valves, e.g. poppet valves having two or more valve-closing members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/26—Systems consisting of a plurality of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting
    • F16C23/041—Sliding-contact bearings self-adjusting with edge relief
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/223—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves with a plurality of valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
    • F02M26/54—Rotary actuators, e.g. step motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only

Definitions

  • the present invention relates to a butterfly valve for controlling the flow rate of a high-temperature fluid, such as an EGR (Exhaust Gas Recirculation) valve and a bypass valve for circulating exhaust gas.
  • a butterfly valve for controlling the flow rate of a high-temperature fluid, such as an EGR (Exhaust Gas Recirculation) valve and a bypass valve for circulating exhaust gas.
  • valve shaft holes are formed in a direction crossing the extending direction of the fluid passage of the housing, and both end portions of the valve shaft of the butterfly valve are respectively inserted into the valve shaft holes, A bearing portion was provided to support the rotation (see, for example, Patent Document 1).
  • the present invention has been made in order to solve the above-described problems, and is a butterfly capable of suppressing an increase in fluid leakage while avoiding deterioration and sticking of a valve shaft when a coaxial shift of a bearing portion occurs.
  • the object is to provide a valve.
  • a butterfly valve includes a housing provided with a fluid passage, two bearing portions provided at opposite positions of the housing sandwiching the fluid passage, and a shaft rotatably held by the two bearing portions. And a valve fixed to the shaft and rotated integrally to open and close the fluid passage, and the inner diameter of the bearing portion is gradually expanded along the axial direction of the shaft.
  • the present invention by making the inner diameter of the bearing portion gradually expand along the axial direction of the shaft, while avoiding deterioration of the shaft and sticking when a coaxial shift of the bearing portion occurs, An increase in fluid leakage can be suppressed.
  • FIG. 6 is a cross-sectional view showing a thermal deformation example of the housing according to the first embodiment. It is a figure explaining the shape of the bearing part of Embodiment 1.
  • FIG. It is sectional drawing to which the spring of Embodiment 1 and its peripheral structure were expanded. It is sectional drawing to which the power transmission member of Embodiment 1 and its peripheral structure were expanded.
  • Embodiment 1 FIG.
  • the butterfly valve shown in FIG. 1 includes a housing 10 that is interposed in a pipe (not shown) that circulates a fluid, a shaft 20 that is rotatably supported by the housing 10, and a fluid that rotates integrally with the shaft 20.
  • Butterfly-shaped valves 21 and 22 for opening and closing the passages 11 and 12.
  • the valves 21 and 22 are attached to the shaft 20 at different angles. In the illustrated example, when one valve 21 (or valve 22) opens the fluid passage 11 (or fluid passage 12), the other valve 22 is opened. (Or valve 21) closes fluid passage 12 (or fluid passage 11).
  • the housing 10 is formed with one fluid inlet 13 and two fluid outlets 14 and 15.
  • the fluid passage 11 communicates the fluid inlet 13 and the fluid outlet 14, and the fluid passage 12 communicates the fluid inlet 13 and the fluid outlet 15.
  • a hole that penetrates the shaft 20 is formed in the housing 10.
  • These bearing holders 16 and 17 are provided with bearing parts 18 and 19 that slidably support the shaft 20, and the opening of the bearing holder 17 is closed with a cap.
  • the one end portion of the shaft 20 penetrates the bearing holding portion 16 and protrudes out of the housing 10, and is connected to the power transmission members 32a to 32c of the actuator 30.
  • the forward drive force or reverse drive force of the motor 31 is transmitted to the shaft 20 through the power transmission members 32a to 32c, and the shaft 20 and the valves 21 and 22 rotate integrally to open and close the fluid passages 11 and 12. .
  • a spring 33 between the housing 10 and the shaft 20 is used to suppress the rattling of the shaft 20 due to vibration and fluid force, and to return the shaft 20 to a specified rotational position when the actuator 30 fails. Is installed.
  • FIG. 2 is a cross-sectional view showing a thermal deformation example of the housing 10 and shows a portion where the stress is large in a dark color.
  • the bearing portion 18a shown in FIG. 3A is a cylinder having an inner diameter of 8.0 (the unit is all [mm]). It is estimated that the maximum outer diameter at which the shaft 20 is not fixed and sliding is not deteriorated is 6.4 when a coaxial shift occurs in the bearing holders 16 and 17 (not shown). Therefore, in order to avoid sticking and deterioration of sliding, the normal clearance between the bearing portions 18a and 19a of the shaft 20 needs to be 1.6 at a minimum.
  • the bearing portions 18b and 19b shown in FIG. 3B have a cylindrical shape in which the inner diameter on the side far from the fluid passages 11 and 12 is 8.0, and the inner diameter gradually increases as the fluid passages 11 and 12 are approached. It is.
  • the maximum outer diameter of the shaft 20 that is not fixed and deteriorated even when the same coaxial displacement as that in FIG. 3A occurs is estimated to be 6.9. Therefore, the clearance can be set as small as 1.1. Therefore, shaft leakage can be suppressed as compared with the case of FIG.
  • the bearing portions 18c and 19c shown in FIG. 3 (c) are cylinders whose inner diameter on the side close to the fluid passages 11 and 12 is 8.0 and whose inner diameter gradually increases as the distance from the fluid passages 11 and 12 increases. .
  • the maximum outer diameter of the shaft 20 that is not fixed and does not deteriorate even when the same coaxial displacement as that in FIG. 3A occurs is estimated to be 6.9. Therefore, the clearance can be set as small as 1.1. Therefore, shaft leakage can be suppressed as compared with the case of FIG.
  • the shape of the bearing portions 18c and 19c can reduce the clearance between the shaft 20 on the side closer to the fluid passages 11 and 12 when a coaxial shift occurs. It is also possible to suppress the sheet leakage that occurs through this clearance when fully closed.
  • the bearing portions 18d and 19d shown in FIG. 3 (d) are cylinders in which the inner diameter of the central portion in the axial direction is 8.0, and the inner diameter gradually increases toward both ends.
  • the maximum outer diameter of the shaft 20 that is not fixed and does not deteriorate when the same coaxial displacement as that in FIG. 3A occurs is estimated to be 7.4. Therefore, the clearance can be set as small as 0.6. Therefore, shaft leakage can be suppressed as compared with the case of FIG. 3 (b) and FIG. 3 (c) as well as FIG. 3 (a).
  • the shape of the bearing portions 18d and 19d eliminates the directionality when the bearing portions 18d and 19d are installed on the bearing holding portions 16 and 17, thereby facilitating assembly work.
  • FIG. 3 in order to explain easily the influence which the difference in the inner surface shape of a bearing part has on a clearance, the result of a simulation under a large numerical condition is shown.
  • FIG. 1 and FIG. 4 and FIG. 5 to be described below are expressed more seriously than actual in order to show the shapes of the inner peripheral surfaces of the bearing portions 18 and 19.
  • the bearing portions 18 and 19 in FIG. 1 have the same shape as the bearing portions 18d and 19d in FIG. 3D, and the actual clearance with the shaft 20 is about several ⁇ m.
  • FIG. 4 is an enlarged cross-sectional view of the spring 33 and its peripheral structure. Since the housing 10 through which the high-temperature gas is circulated becomes hot, if the spring 33 is installed directly on the housing 10, a heat sink occurs. However, if the spring 33 is installed away from the housing 10, the entire length of the butterfly valve is extended. Therefore, the influence of high heat is reduced by installing the spring holder 34 on the housing 10 and installing the spring 33 on the spring holder 34 instead of installing the spring 33 directly on the housing 10.
  • the spring holder 34 includes an outer cylinder portion 35 that covers the outside of the spring 33, an inner cylinder portion 36 that covers the inside of the spring 33, and a gap between the outer cylinder portion 35 and the inner cylinder portion 36 on the side close to the fluid passage 11.
  • the bottom portion 37 is closed, and a holder fixing portion 38 that fixes the outer cylinder portion 35 to the housing 10.
  • a convex portion 39 is formed on the outer periphery of the bearing holding portion 16 in the housing 10.
  • the spring holder 34 is arrange
  • a holder fixing portion 38 is formed at a position farthest from the fluid passage 11, that is, at the open end portions of the inner cylinder portion 36 and the outer cylinder portion 35.
  • the spring holder 34 Since the spring holder 34 is in a state where the portions other than the holder fixing portion 38 are separated from the housing 10 (the bearing holding portion 16 and the convex portion 39), the heat of the hot gas flowing through the fluid passage 11 is directly transmitted from the housing 10. Absent. Moreover, the heat transmitted from the bearing holding part 16 to the spring 33 is suppressed by extending the inner cylinder part 36 in the axial direction.
  • the spring holder 34 is a component that holds a hook (not shown) on the fixed side of the spring 33, and is less worn due to relative displacement with the spring 33.
  • the other hook (not shown) of the spring 33 is held by the power transmission member 32c, and the urging force of the spring 33 is transmitted to the shaft 20 via the power transmission member 32c.
  • a guide member 40 and a guide member 41 are provided as a guide for preventing the top end of the torsion spring portion of the spring 33 from falling.
  • One guide member 40 is an annular member that is in sliding contact with the end portion of the spring 33, and is placed on the torsion spring portion to receive an urging force in the axial direction and is pressed against the power transmission member 32c.
  • the guide member 41 is fixed to the shaft 20 with an inner diameter, and when the torsion spring part falls down, the guide member 40 slidably in contact with the torsion spring part also moves in the radial direction and contacts the guide member 41. Since the movement of the is restricted, the fall can be prevented.
  • the guide member 40 and the guide member 41 are formed as separate members so that the guide member 40 in contact with the spring 33 is not directly attached to the shaft 20, thereby reducing heat transmitted from the shaft 20 to the spring 33. Furthermore, a ratchet 42 is provided on the peripheral edge of the guide member 41.
  • This screw turn 42 is a peripheral wall projecting from the peripheral portion of the guide member 41 toward the fluid passage 11, and the hot gas leaked from the clearance between the shaft 20 and the bearing portion 18 is removed from the guide member 40 and the guide member 40.
  • the spring 33 is also prevented from sag due to leaked gas.
  • the leaked gas guided by the ratchet 42 is discharged to the outside through a gap between the bearing holder 16 and the spring holder 34.
  • the mouse turn 42 is formed on the guide member 41, but may be formed on the guide member 40.
  • FIG. 5 is an enlarged cross-sectional view of the power transmission member 32c and its peripheral structure. Since the actuator 30 having the motor 31 has low heat resistance, it is better to reduce heat transfer from the housing 10 as much as possible. Therefore, the actuator 30 is not directly attached to the housing 10, but is attached via the heat insulating member 43.
  • a stainless steel pipe having a low thermal conductivity is used as the heat insulating member 43 so that only both ends of the pipe are in contact with the housing 10 and the base plate 45. Thereby, the actuator 30 can be mounted away from the housing 10, and heat transfer from the housing 10 to the actuator 30 can be reduced.
  • the surface of the housing 10 facing the actuator 30 is covered with a cover 44 so as to block the radiant heat of the housing 10 and the leaked gas.
  • the cover 44 may be made of a material having high thermal conductivity to improve heat dissipation.
  • holes for inserting bolts 46 are formed in the cover 44 and the base plate 45 of the actuator 30, and screw holes for fastening the bolts 46 are formed in the housing 10.
  • a contact portion 47 that is one step higher is formed around the insertion hole of the cover 44, and only the contact portion 47 is in contact with the base plate 45, and other portions are separated from the base plate 45. Thereby, a gap is formed between the cover 44 and the base plate 45, and heat transfer from the cover 44 to the base plate 45 to which the actuator 30 is attached can be reduced.
  • the butterfly valve includes the housing 10 provided with the fluid passages 11 and 12, and the bearing portions 18 and 19 provided at the opposing positions of the housing 10 across the fluid passages 11 and 12.
  • the shaft 20 is rotatably held by the bearings 18 and 19, and the valves 21 and 22 are fixed to the shaft 20 and rotate integrally to open and close the fluid passages 11 and 12.
  • the inner diameter of 19 is configured to gradually widen along the axial direction of the shaft 20. For this reason, it is possible to suppress an increase in fluid leakage while avoiding deterioration and sticking of the shaft 20 when a coaxial shift of the bearing portions 18 and 19 occurs.
  • bearing portion 18c when the bearing portions 18 and 19 are formed so as to gradually expand along the axial direction of the shaft 20 so that the inner diameter near the fluid passages 11 and 12 is small and the inner diameter on the far side is large (bearing portion 18c). 19c) has the effect of suppressing leakage of the seat flowing from the upstream side to the downstream side via the clearance between the shaft 20 and the bearing portions 18 and 19 when the valve 21 or the valve 22 is fully closed. . Further, when the bearing portions 18 and 19 are formed so as to gradually expand toward both ends along the axial direction of the shaft 20 so that the inner diameter of the center portion is small and the inner diameters of both ends are large (bearing portions 18d, 19d) has the effect of facilitating assembly work in addition to the above effects.
  • the butterfly valve is fixed to the shaft 20 inside the guide member 40 and the annular guide member 40 that is in sliding contact with the end of the spring 33 installed on the outer periphery of the shaft 20.
  • the guide member 41 is configured such that the outer peripheral portion abuts on the inner peripheral portion of the guide member 40 and restricts the radial movement of the guide member 40, and the screw 42 is formed on the outer peripheral portion of the guide member 41. For this reason, propagation of heat from the shaft 20 can be reduced while suppressing the fall of the spring 33. Moreover, since the high temperature gas leaked from the bearing portion 18 can be released in a direction not directly hitting the spring 33 by the screw return 42, the heat settling of the spring 33 can be suppressed.
  • the butterfly valve is provided with the spring holder 34 that accommodates the spring 33 around the hole of the housing 10 that penetrates the end of the shaft 20.
  • the inner cylinder part 36 that covers the inner side of the inner side 33, the outer cylinder part 35 that covers the outer side, and the bottom part 37 that closes the gap between the inner cylinder part 36 and the outer cylinder part 35, the inner cylinder part 36 and the outer cylinder part 35 is fixed to the convex portion 39 of the housing 10 by the holder fixing portion 38 on the open side, and the other portions are separated from the housing 10. For this reason, the heat propagated from the housing 10 to the spring 33 can be reduced.
  • the butterfly valve is provided between the actuator 30 that rotationally drives the shaft 20, and between the actuator 30 and the housing 10, and the heat insulation that holds the actuator 30 in a state of being separated from the housing 10.
  • the member 43 is provided. For this reason, heat transfer to the actuator 30 having low heat resistance can be reduced as much as possible.
  • the butterfly valve is configured to include the cover 44 that covers the surface of the housing 10 that faces the actuator 30, so that the radiant heat and leakage gas of the housing 10 are blocked, The low actuator 30 can be protected.
  • the butterfly valve is configured to provide a gap between the base plate 45 to which the actuator 30 is attached and the cover 44, so that heat transfer from the cover 44 to the actuator 30 can be reduced. it can.
  • any constituent element of the embodiment can be modified or any constituent element of the embodiment can be omitted within the scope of the invention.
  • Embodiment 1 described above an example in which the present invention is applied to a butterfly valve configured to open and close a fluid passage that is bifurcated by two valves fixed to a shaft has been described. You may apply to the butterfly valve of the structure which opens and closes one fluid channel
  • the housing is asymmetrical on the upstream side and the downstream side, a coaxial shift is likely to occur. Therefore, even in the case of a butterfly valve having one valve and one fluid passage, the housing is asymmetrical. The effect of the invention becomes remarkable. Further, since the coaxial displacement of the bearing portion tends to increase as the shaft becomes longer, the effect of the present invention becomes more remarkable as the number of valves increases (that is, as the shaft becomes longer).
  • the butterfly valve according to the present invention is adapted to be used for an EGR valve that circulates exhaust gas at a high temperature (500 ° C. to 800 ° C.) because the effect of high temperature is reduced.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lift Valve (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Valve Housings (AREA)

Abstract

Eléments de roulement (18, 19) dont la forme s'élargit progressivement le long de la direction axiale d'un arbre (20) vers les deux extrémités de sorte que le diamètre intérieur de la partie centrale est petit et celui des deux parties d'extrémité est grand. La dégradation du mouvement coulissant et l'adhérence de l'arbre (20) sont évitées lorsqu'un boîtier est déformé et qu'un déplacement coaxial s'est produit.
PCT/JP2012/000037 2012-01-05 2012-01-05 Vanne papillon Ceased WO2013102951A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2012/000037 WO2013102951A1 (fr) 2012-01-05 2012-01-05 Vanne papillon
JP2013552330A JP5714135B2 (ja) 2012-01-05 2012-01-05 バタフライバルブ
US14/350,423 US20140252259A1 (en) 2012-01-05 2012-01-05 Butterfly valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/000037 WO2013102951A1 (fr) 2012-01-05 2012-01-05 Vanne papillon

Publications (1)

Publication Number Publication Date
WO2013102951A1 true WO2013102951A1 (fr) 2013-07-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/000037 Ceased WO2013102951A1 (fr) 2012-01-05 2012-01-05 Vanne papillon

Country Status (3)

Country Link
US (1) US20140252259A1 (fr)
JP (1) JP5714135B2 (fr)
WO (1) WO2013102951A1 (fr)

Cited By (3)

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CN105276202A (zh) * 2015-10-08 2016-01-27 瑞安市阀门一厂 气动快开百叶蝶阀
JP2017101626A (ja) * 2015-12-03 2017-06-08 愛三工業株式会社 スロットル装置
KR20240029939A (ko) * 2022-08-29 2024-03-07 캄텍주식회사 차량용 밸브

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CN107076327B (zh) * 2014-10-31 2018-11-20 三菱电机株式会社 流体控制阀
CN104373255A (zh) * 2014-11-21 2015-02-25 无锡隆盛科技股份有限公司 电动egr阀动力部分保护结构
EP3234421A1 (fr) * 2014-12-19 2017-10-25 Continental Automotive GmbH Dispositif de soupape dans un véhicule automobile
US10400817B2 (en) 2016-11-22 2019-09-03 Woodward, Inc. Radial bearing device
FR3080427B1 (fr) * 2018-04-24 2020-04-03 Faurecia Systemes D'echappement Vanne pour une ligne d'echappement
DE102018214069A1 (de) * 2018-08-21 2020-02-27 Continental Automotive Gmbh Ventil zur Steuerung von Abgas oder Frischluft in einer Antriebseinheit eines Kraftfahrzeuges oder Generators
US11022079B1 (en) * 2020-02-21 2021-06-01 Deere & Company Dual element engine gas valve
US12123379B2 (en) * 2022-03-28 2024-10-22 Deere & Company Dual core exhaust gas recirculation cooler
KR102455463B1 (ko) * 2022-04-29 2022-10-17 캄텍주식회사 차량용 3웨이 밸브
US20250012327A1 (en) * 2023-07-03 2025-01-09 Hanon Systems Combination seal and bearing
WO2025072011A1 (fr) * 2023-09-28 2025-04-03 Oil States Industries, Inc Ensemble vannes couplées

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0256975U (fr) * 1988-10-19 1990-04-24
JP2005256971A (ja) * 2004-03-12 2005-09-22 Kitz Corp バタフライ弁
JP2010071397A (ja) * 2008-09-19 2010-04-02 Aisan Ind Co Ltd 軸受装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3038282B2 (ja) * 1993-04-12 2000-05-08 株式会社日立製作所 スロットル弁開閉装置
US5427141A (en) * 1994-09-19 1995-06-27 Fuji Oozx Inc. Pressure fluid control valve device
JP2002339766A (ja) * 2001-05-15 2002-11-27 Aisan Ind Co Ltd スロットル弁制御装置
WO2004090360A1 (fr) * 2003-04-02 2004-10-21 Mitsubishi Materials Corporation Palier fritte impregne d'huile et procede de production de celui-ci
US7303481B2 (en) * 2005-02-04 2007-12-04 Itt Manufacturing Enterprises, Inc. Electrically isolated actuator output shaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0256975U (fr) * 1988-10-19 1990-04-24
JP2005256971A (ja) * 2004-03-12 2005-09-22 Kitz Corp バタフライ弁
JP2010071397A (ja) * 2008-09-19 2010-04-02 Aisan Ind Co Ltd 軸受装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105276202A (zh) * 2015-10-08 2016-01-27 瑞安市阀门一厂 气动快开百叶蝶阀
JP2017101626A (ja) * 2015-12-03 2017-06-08 愛三工業株式会社 スロットル装置
KR20240029939A (ko) * 2022-08-29 2024-03-07 캄텍주식회사 차량용 밸브
KR102743614B1 (ko) * 2022-08-29 2024-12-17 캄텍주식회사 차량용 밸브

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